Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
  • F16C33/02—Parts of sliding-contact bearings
  • F16C33/04—Brasses; Bushes; Linings
  • F16C33/06—Sliding surface mainly made of metal
  • F16C33/10—Construction relative to lubrication
  • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
  • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
  • F16C33/1065—Grooves on a bearing surface for distributing or collecting the liquid
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C17/00—Sliding-contact bearings for exclusively rotary movement
  • F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
• • H—ELECTRICITY
  • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
  • H02K—DYNAMO-ELECTRIC MACHINES
  • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
  • H02K7/08—Structural association with bearings

Definitions

• the present invention relates to the field of rotating machines. It relates to a bearing for the rotor of a rotating machine according to the preamble of claim 1.
• Such a warehouse is e.g. known from CH-A5-651 362.
• the rotors of large rotating machines such as hydrogen generators are usually supported by hydrodynamic plain bearings. With these bearings, the axial and radial guidance is carried out by separate bearings of different designs. A partial summary of these separate Bearing is possible insofar as a race running in an axial bearing additionally absorbs radial forces by arranging radial guide segments around it. Such a configuration, as is known from CH-A5-651 362 mentioned at the outset (see FIG. 1 there), is reproduced in a greatly simplified form in FIG. 1. In the rotating machine 10 'of FIG. 1, the rotor with the rotor shaft 12 is rotatably mounted about a vertical axis of rotation 11.
• a race 14 ' is fastened to the rotor shaft 12 via a flange 13, which slides with the underside on the sliding surface 20 of an axial bearing or support bearing 17 consisting of individual segments (vertical arrows in FIG. 1).
• the axial bearing 17 is in turn supported by a support 18 in the axial direction.
• the radial bearing 15 is in turn supported by supports 16 in the radial direction.
• the axial bearing 17 and the radial bearing or guide bearing 15 function independently of one another in this known configuration. Both camps run in an oil bath.
• the function "carrying the rotor” is performed by the axial bearing 17, the function “guiding the rotor” is performed by the guide or radial bearing 15. Both camps have their own segments that are adapted to their respective functions.
• a disadvantage of the known bearing with the separate bearing functions is that the thickness of the race in the axial direction must be chosen large enough to enable the radial bearing arranged on the side of the race. This makes the machine longer overall in the axial direction.
• the object is achieved by the entirety of the features of claim 1.
• the essence of the invention is to combine the previously separate radial bearing and thrust bearing (or their bearing segments) into a combined radial and thrust bearing which simultaneously has axial sliding surfaces and radial sliding surfaces.
• the two sliding surfaces are arranged on the same bearing (or bearing segment) , This enables a simplified, more compact construction of the bearing, in which the friction losses can be reduced at the same time by a clever arrangement of the sliding surfaces.
• a first preferred embodiment of the invention is characterized in that the combined radial and axial bearing comprises a plurality of individual bearing segments, which have the shape of circular ring sections and are arranged spaced apart from one another in a ring around the axis of rotation, that an axial one on each of the bearing segments Slide surface and a radial slide surface are formed, and that each bearing segment has its own radial support.
• the combined radial and axial bearing is arranged in an oil bath.
• Another alternative is characterized in that means for supplying lubricating oil are provided in the bearing segments, said lubricating oil exiting onto the sliding surfaces through outlet openings in the axial and radial sliding surfaces, preferably a first outlet opening being provided in the axial sliding surface in each bearing segment, which has the shape of an elongated slot extending in the radial direction and is arranged in the direction of rotation, at the beginning of the axial sliding surface, and wherein in each bearing segment there is a second outlet opening in the radial sliding surface, which has the shape of an extending in the axial direction has elongated slot and is arranged in the direction of rotation at the beginning of the radial sliding surface.
• the outlet openings of each bearing segment are preferably connected to a common oil supply bore via connecting channels.
• the bearing arrangement according to the invention is further simplified and is characterized by reduced friction losses if, according to another advantageous embodiment, the rotor has a rotor shaft, if a rotor ring concentrically surrounding the rotor shaft is fastened to the rotor shaft, with which the rotor on the axial sliding surfaces of the combined radial - And thrust bearing slides, and when the rotor slides with the rotor shaft itself on the radial sliding surfaces of the combined radial and thrust bearing.
• Fig. 2 in a representation comparable to Fig. 1, a bearing with a combined radial and axial bearing according to a preferred
• FIG. 3 in a perspective view in the radial direction an individual
• Bearing segment of the bearing shown in Fig. 2 in which lubricating oil is specifically supplied to the sliding surfaces within the bearing segment.
• FIG. 2 shows a bearing with a combined radial and axial bearing according to a preferred embodiment of the invention in a representation comparable to FIG. 1.
• the same parts are largely denoted by the same reference numerals.
• the rotating machine 10 rotates with a rotor, of which a part of the rotor shaft 12 is shown in FIG. 2, about the vertical axis of rotation 11.
• a race 14 is attached to the rotor shaft 13, which is used exclusively for the axial bearing serves. It can therefore be significantly reduced in its axial thickness compared to the race 14 'from FIG. 1.
• the rotor slides with the race 14 on the upper, axial (horizontal) sliding surface 24 of a combined radial and axial bearing 21 (composed of bearing segments), which in turn is supported in the axial direction by an axial support 23.
• the combined radial and axial bearing 21 is extended in the radial direction towards the rotor shaft 12 to such an extent that a radial (vertical) sliding surface 25 can be formed, on which the rotor shaft 12 is guided.
• the combined radial and axial bearing 21 is supported in the radial direction by a radial support 22. Since the radial sliding surface 25 ter lies inside, as the radial sliding surface 19 in the known bearing from FIG. 1, results in a much lower peripheral speed at the same speed, which leads to lower friction losses and thus less heating.
• the combined radial and axial bearing 21 preferably consists of individual bearing segments 26 according to FIG. 3, which have the shape of circular ring sections and are arranged at a distance from one another in a ring around the axis of rotation 11 or rotor shaft 12.
• An axial sliding surface 24 and a radial sliding surface 25 are formed on each of the bearing segments 26.
• Each of the bearing segments 26 has its own radial support 22, the force introduction surface of which is indicated by a circle in FIG. 3.
• the combined radial and axial bearing 21 can in principle be arranged in an oil bath.
• means 29,..., 32 for supplying lubricating oil are preferably provided in the bearing segments 26 according to FIG. 3, the lubricating oil exiting onto the sliding surfaces 24, 25 through outlet openings 27, 28 in the axial and radial sliding surfaces 24 and 25, respectively.
• the means comprise a first outlet opening 27, which has the shape of an elongated slot extending in the radial direction and is arranged at the beginning of the axial sliding surface 24 when viewed in the direction of rotation.
• the lubricating oil emerging through the slot is thus distributed on the sliding surface 24 in the form of a lubricating film by the bearing ring 14 sliding over the sliding surface 24.
• a second outlet opening 28 is provided in the radial sliding surface 25, which has the shape of an elongated slot extending in the axial direction and is arranged at the beginning of the radial sliding surface 25, as seen in the direction of rotation.
• the lubricating oil emerging from the outlet openings 27, 28 is supplied from a rear connection 32 via a radial oil supply bore 31 arranged in the interior of the bearing segment 26 and distributed to the outlet openings 27, 28 via connecting channels 29, 30.
• a radial oil supply bore 31 arranged in the interior of the bearing segment 26 and distributed to the outlet openings 27, 28 via connecting channels 29, 30.
• the bearing takes up less space in the axial direction. The whole machine can therefore be built lower.
• the radial bearing has a smaller radius towards the shaft. This means a lower peripheral speed and therefore lower friction losses.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Chemical & Material Sciences (AREA)
• Oil, Petroleum & Natural Gas (AREA)
• Power Engineering (AREA)
• Sliding-Contact Bearings (AREA)
• Rotary Pumps (AREA)
• Applications Or Details Of Rotary Compressors (AREA)
• Supercharger (AREA)

Priority Applications (5)

Applications Claiming Priority (2)

Publications (1)

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Cited By (3)

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Citations (6)

Family Cites Families (2)

• 2003
  • 2003-06-06 DE DE50309372T patent/DE50309372D1/de not_active Expired - Lifetime
  • 2003-06-06 AT AT03727866T patent/ATE389120T1/de not_active IP Right Cessation
  • 2003-06-06 ES ES03727866T patent/ES2301796T3/es not_active Expired - Lifetime
  • 2003-06-06 RU RU2005101078/11A patent/RU2319045C2/ru not_active IP Right Cessation
  • 2003-06-06 WO PCT/IB2003/002364 patent/WO2004001241A1/de active IP Right Grant
  • 2003-06-06 BR BR0312431-2A patent/BR0312431A/pt not_active IP Right Cessation
  • 2003-06-06 EP EP03727866A patent/EP1514033B1/de not_active Expired - Lifetime
  • 2003-06-06 CN CNB038197936A patent/CN100460696C/zh not_active Expired - Fee Related
  • 2003-06-06 AU AU2003233114A patent/AU2003233114A1/en not_active Abandoned
  • 2003-06-06 CA CA002489699A patent/CA2489699A1/en not_active Abandoned

Patent Citations (6)

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